CN201569204U - Air conditioning system capable of balancing refrigerant amount - Google Patents
Air conditioning system capable of balancing refrigerant amount Download PDFInfo
- Publication number
- CN201569204U CN201569204U CN2009203167542U CN200920316754U CN201569204U CN 201569204 U CN201569204 U CN 201569204U CN 2009203167542 U CN2009203167542 U CN 2009203167542U CN 200920316754 U CN200920316754 U CN 200920316754U CN 201569204 U CN201569204 U CN 201569204U
- Authority
- CN
- China
- Prior art keywords
- refrigerant
- fluid reservoir
- heat exchanger
- check valve
- capillary
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The utility model relates to an air conditioning system capable of balancing refrigerant amount, which comprises a compressor, a four-way valve, an air-liquid separator, an indoor heat exchanger, an outdoor heat exchanger, a throttle device and pipelines which are used to connect the parts, the system further comprises a liquid storage tank, wherein the input end of the liquid storage tank is connected with an outlet of the outdoor heat exchanger, the outlet end of the liquid storage tank is connected with the inlet end of the throttle device through a one-way valve, the flow direction of the one-way valve is same to the flow direction of refrigerant when an air conditioning refrigeration operates, and a second one-way valve or a capillary tube is arranged between the input end of the liquid storage tank and the flow out end of the one-way valve and then is connected in parallel. The system achieves the storage of a certain liquid refrigerant in the liquid storage tank when refrigeration operating through using different flow directions of the refrigerant when cooling and heating operating, the liquid storage tank does not store the refrigerant when heating operating, thereby being capable of inputting all refrigerant into the operating, balancing the flow rate of the refrigerant when cooling and heating operating, and leading the air conditioning to achieve a best energy efficiency ratio when cooling and heating.
Description
Technical field
The utility model relates to a kind of air-conditioner cooling cycle system, but particularly a kind of air-conditioning system of balance coolant quantity belongs to the domestic air conditioning technical field.
Background technology
Air conditioner circulating system generally comprises compressor, condenser, throttling arrangement, evaporimeter, gas-liquid separator, cross valve, reaches the pipeline that connects each parts, cold-producing medium circulates in this system, realize refrigerating operaton or heating operation, regulate indoor environment temperature and humidity, guarantee that indoor environment temperature and humidity reach setting value.The cold-producing medium that generally adopts is R22 at present, because the material impact of depletion of the ozone layer and global warming, progressively replace R22 with R410A now, for each cooling cycle system, the charging amount of its cold-producing medium is certain, as being the air-conditioner of 2500W for specified refrigerating capacity, the charging amount of cold-producing medium is generally about 700g, is the air-conditioner of 3500W for specified refrigerating capacity, and the charging amount of cold-producing medium is generally about 900g, use R410A and R22, the charging amount difference of cold-producing medium is little.
Air-conditioner is when carrying out normal refrigerating operaton and heating operation, because the system matches situations such as heat exchange area of indoor heat exchanger and outdoor heat exchanger is different, for obtain best refrigeration efficiency than and heating energy efficiency ratio, air-conditioner needed refrigerant amount when refrigerating operaton is different often with needed refrigerant amount when the heating operation.Yet, because air-conditioner its refrigerant charge when dispatching from the factory is certain, so for each air-conditioning system, can only guarantee that refrigeration efficiency ratio or one of them performance of heating energy efficiency ratio are in optimum value.
Obtain best refrigeration efficiency ratio and heating energy efficiency ratio simultaneously in order to try one's best, the method that generally adopts is at present, adopt method by the heat exchange area that changes evaporimeter or condenser, make the heat exchange area and the refrigerant charge of two devices be complementary, thereby under the situation that guarantees refrigeration efficiency ratio or heating energy efficiency ratio, improve other heating energy efficiency ratio or refrigeration efficiency ratio as far as possible, but there is deficiency in this mode, because the shell sizes of air conditioner room unit and off-premises station is certain, can not arbitrarily change, so that also relative fixed of the size of two devices, the scope of change is subjected to great restriction, also is difficult to control.
Summary of the invention.
The utility model main purpose is to address the above problem and is not enough, but provide a kind of air-conditioning system of balance coolant quantity, it is simple in structure, easy to use, can the balanced system cold operation and the refrigerant flow during heating operation, make the air-conditioner refrigeration and heat Shi Junneng to reach best Energy Efficiency Ratio.
For achieving the above object, the technical solution of the utility model is:
But a kind of air-conditioning system of balance coolant quantity, comprise compressor, cross valve, gas-liquid separator, indoor heat exchanger, outdoor heat exchanger, the throttling device, and be used to connect the pipeline of above-mentioned each parts, also comprise a fluid reservoir in this system, the arrival end of described fluid reservoir is connected with the outlet of described outdoor heat exchanger, the port of export of described fluid reservoir is connected with described throttling device arrival end by check valve, refrigerant flow direction when the flow direction of described check valve is moved with air conditioner refrigerating is identical, one second check valve in parallel again or first capillary between the outflow end of the arrival end of described fluid reservoir and check valve, the flow direction of described second check valve is opposite with the flow direction of described check valve.
Further improvement of the utility model is that at the two ends of check valve one second capillary in parallel, described second flow capillaceous is less than described first capillary.
Needed refrigerant amount was poor when the volume of described fluid reservoir was air conditioner refrigerating when operation and heating operation.
Content to sum up, but the air-conditioning system of balance coolant quantity provided by the utility model, fluid reservoir of series connection between outdoor heat exchanger and throttling device, the flow of refrigerant direction is different when utilizing refrigeration with heating operation, when being implemented in refrigerating operaton, a certain amount of liquid refrigerant of storage in the fluid reservoir, and when heating operation, do not store cold-producing medium in the fluid reservoir, put into whole cold-producing mediums in service, like this can the balanced system cold operation and the refrigerant flow during heating operation, make the air-conditioner refrigeration and heat Shi Junneng to reach best Energy Efficiency Ratio.
In addition,, can guarantee when heating operation that a small amount of gas flow is arranged in the fluid reservoir all the time by second capillary is set, effectively avoid lubricating oil to lodge in the fluid reservoir.
It is the air-conditioning system of R410A and R22 that the utility model is suitable for cold-producing medium.
Description of drawings
Fig. 1 the utility model embodiment one air-conditioning system schematic diagram;
Fig. 2 the utility model embodiment two air-conditioning system schematic diagrames.
As depicted in figs. 1 and 2, compressor 1, cross valve 2, gas-liquid separator 3, indoor heat exchanger 4, outdoor heat exchanger 5, throttling device 6, fluid reservoir 7, check valve 8, arrival end 9, the port of export 10, the second check valves 11, the first capillaries 12, the second capillaries 13.
The specific embodiment
Below in conjunction with the accompanying drawing and the specific embodiment the utility model is described in further detail:
As depicted in figs. 1 and 2, air-conditioning system comprises compressor 1, cross valve 2, gas-liquid separator 3, indoor heat exchanger 4, outdoor heat exchanger 5, throttling device 6, interconnect by pipeline between each parts, form a complete refrigerant circulation loop, wherein, throttling device 6 can be a capillary, also can be electric expansion valve, and cold-producing medium can be selected R22 or R410A.
Embodiment one:
As shown in Figure 1, fluid reservoir 7 of series connection in the pipeline between outdoor heat exchanger 5 and throttling device 6, the top of this fluid reservoir 7 has a port of export 10, has an arrival end 9 in its underpart, the arrival end 9 of fluid reservoir 7 is connected with the outlet of outdoor heat exchanger 5, the port of export 10 of fluid reservoir 7 is connected with the arrival end of throttling device 6 by check valve 8, refrigerant flow direction when the flow direction of this check valve 8 is moved with air conditioner refrigerating is identical, one first capillary 12 in parallel again between the outflow end of the arrival end 9 of fluid reservoir 7 and check valve 8 is at the two ends of check valve 8 one second capillary 13 in parallel.
Wherein, the flow of second capillary 13 is less than first capillary 12, the cold-producing medium that guarantees the overwhelming majority flows through from first capillary 12, have only the gaseous refrigerant of minute quantity to flow through from second capillary 13, first capillary 12 and second capillary 13 can be regulated its flow by regulating length capillaceous and internal diameter, for example, if first capillary 12 is identical with the internal diameter of second capillary 13, the length of second capillary 13 will be longer than the length of first capillary 12 far away so; If first capillary 12 is identical with the length of second capillary 13, the internal diameter of second capillary 13 is less than the internal diameter of first capillary 12 so.
When refrigerating operaton, because the internal diameter of first capillary 12 is far smaller than the arrival end 9 of fluid reservoir 7, so, cold-producing medium is through behind the outdoor heat exchanger 5, the cold-producing medium of the overwhelming majority enters fluid reservoir 7 inside by the arrival end 9 of fluid reservoir 7 bottoms, cold-producing medium flows out from the port of export 10 on fluid reservoir 7 tops, enters throttling device 6 through check valve 8.In this process, be full of high pressure liquid refrigerant in the fluid reservoir 7, and when refrigerating operaton, all the time there is a certain amount of cold-producing medium to be stored in the fluid reservoir 7, do not participate in kind of refrigeration cycle, make the refrigerant amount of participation refrigerating operaton and the heat exchange area of indoor heat exchanger 4 and outdoor heat exchanger 5 be complementary, reach best running status when guaranteeing refrigerating operaton.
When heating operation, the flow of refrigerant direction is opposite during with refrigerating operaton, cold-producing medium enters flow controller spare 6 after being flowed out by indoor heat exchanger 4, because the effect of check valve 8, and the flow of second capillary 13 will be much smaller than the flow of first capillary 12, after cold-producing medium passes through throttling device 6 again, the cold-producing medium of the overwhelming majority can be flow through by first capillary 12, direct then inlet chamber external heat exchanger 5, flow through fluid reservoir 7 after having only cold-producing medium than low discharge through second capillary 13, but its flow is far smaller than the flow through first capillary 12, like this, whole nearly cold-producing mediums participates in heating operation, and the same refrigerant amount of participation heating operation and the heat exchange area of indoor heat exchanger 4 and outdoor heat exchanger 5 of making is complementary, and reaches best running status when guaranteeing heating operation.
Because when compressor 1 work, there is a small part refrigeration oil continuously from the cylinder of compressor 1, to be forced out with cold-producing medium, enter in the pipeline and indoor heat exchanger 4 and outdoor heat exchanger 5 of system, when refrigeration oil can not return compressor 1, will cause the pasta of compressor 1 to descend, the phenomenon that compressor 1 oil starvation burns occur.This system is when refrigerating operaton, high pressure liquid refrigerant in the fluid reservoir 7 is constantly to flow, so do not have the phenomenon of trapped fuel, but when heating operation, if there is not cold-producing medium to flow through in the fluid reservoir 7 fully, can cause trapped fuel in the fluid reservoir 7, so, in fluid reservoir 7, there is refrigeration oil, the present invention in the parallel connection of the two ends of check valve 8 one second capillary 13, when heating operation, the cold-producing medium that comes out from throttling device 6 is the gas-liquid mixed state, wherein has a spot of cold-producing medium can enter second capillary 13, enter then in the fluid reservoir 7, like this, can guarantee to have all the time in the fluid reservoir 7 a certain amount of cold-producing medium to flow in jar, refrigeration oil just can not remain in the fluid reservoir 7.
Needed refrigerant amount was poor when the volume of fluid reservoir 7 was air conditioner refrigerating when operation and heating operation, for example, for specified refrigerating capacity is the air-conditioner of 2500W, the charging amount of cold-producing medium is generally about 700g, has best refrigeration efficiency ratio in the time of refrigerating operaton can only being guaranteed like this, and heating energy efficiency ratio is just relatively low, so in the present embodiment, the charging amount of cold-producing medium can increase to about 800g, reach optimal operational condition when guaranteeing heating operation, and when refrigerating operaton, with unnecessary 100g left and right sides cold-producing medium, be stored in the fluid reservoir 7, at this moment, the volume of fluid reservoir 7 calculates by the cold-producing medium of storage 100g.
Embodiment two:
Fluid reservoir 7 of series connection in the pipeline between outdoor heat exchanger 5 and throttling device 6, the top of this fluid reservoir 7 has a port of export 10, has an arrival end 9 in its underpart, the arrival end 9 of fluid reservoir 7 is connected with the outlet of outdoor heat exchanger 5, the port of export 10 of fluid reservoir 7 is connected with the arrival end of throttling device 6 by check valve 8, refrigerant flow direction when the flow direction of this check valve 8 is moved with air conditioner refrigerating is identical, the flow direction of one second check valve 11, the second check valves 11 in parallel again is opposite with the flow direction of above-mentioned check valve 8 between the outflow end of the arrival end 9 of fluid reservoir 7 and check valve 8.
When refrigerating operaton, because the guide effect of second check valve 11, cold-producing medium can only be entered fluid reservoir 7 inside by the arrival end 9 of fluid reservoir 7 bottoms through behind the outdoor heat exchanger 5, cold-producing medium flows out from the port of export 10 on fluid reservoir 7 tops, enters throttling device 6 through check valve 8.In this process, be full of high pressure liquid refrigerant in the fluid reservoir 7, and when refrigerating operaton, had a certain amount of cold-producing medium to be stored in the fluid reservoir 7 all the time, do not participated in kind of refrigeration cycle.
When heating operation, the flow of refrigerant direction is opposite during with refrigerating operaton, cold-producing medium enters flow controller spare 6 after being flowed out by indoor heat exchanger 4, because the effect of check valve 8, after cold-producing medium passes through throttling device 6 again, second check valve 11 of can only flowing through, direct then inlet chamber external heat exchanger 5, cold-producing medium does not flow through fluid reservoir 7, and all cold-producing medium participates in heating operation.
For fear of fluid reservoir 7 interior trapped fuel, in the parallel connection of the two ends of check valve 8 one second capillary 13, when heating operation, the cold-producing medium that comes out from throttling device 6 is the gas-liquid mixed state, wherein there is a spot of gaseous refrigerant can enter second capillary 13, enters then in the fluid reservoir 7, like this, can guarantee to have all the time in the fluid reservoir 7 a certain amount of gaseous refrigerant to flow in jar, refrigeration oil just can not remain in the fluid reservoir 7.
As mentioned above, given in conjunction with the accompanying drawings and embodiments scheme content can derive the similar techniques scheme.In every case be the content that does not break away from technical solutions of the utility model, to any simple modification, equivalent variations and modification that above embodiment did, all still belong in the scope of technical solutions of the utility model according to technical spirit of the present utility model.
Claims (3)
1. but the air-conditioning system of a balance coolant quantity, comprise compressor (1), cross valve (2), gas-liquid separator (3), indoor heat exchanger (4), outdoor heat exchanger (5), throttling device (6), and be used to connect the pipeline of above-mentioned each parts, it is characterized in that: also comprise a fluid reservoir (7) in this system, the arrival end (9) of described fluid reservoir (7) is connected with the outlet of described outdoor heat exchanger (5), the port of export (10) of described fluid reservoir (7) is connected with described throttling device (6) arrival end by check valve (8), refrigerant flow direction when the flow direction of described check valve (8) is moved with air conditioner refrigerating is identical, one second check valve in parallel again (11) or first capillary (12) between the outflow end of the arrival end (9) of described fluid reservoir (7) and check valve (8), the flow direction of described second check valve (11) is opposite with the flow direction of described check valve (8).
2. but the air-conditioning system of balance coolant quantity as claimed in claim 1 is characterized in that: the two ends of described check valve (8) one second capillary (13) in parallel, the flow of described second capillary (13) is less than described first capillary (12).
3. but the air-conditioning system of balance coolant quantity as claimed in claim 1 or 2 is characterized in that: needed refrigerant amount was poor when the volume of described fluid reservoir (7) was air conditioner refrigerating when operation and heating operation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009203167542U CN201569204U (en) | 2009-12-08 | 2009-12-08 | Air conditioning system capable of balancing refrigerant amount |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009203167542U CN201569204U (en) | 2009-12-08 | 2009-12-08 | Air conditioning system capable of balancing refrigerant amount |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201569204U true CN201569204U (en) | 2010-09-01 |
Family
ID=42661494
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009203167542U Expired - Lifetime CN201569204U (en) | 2009-12-08 | 2009-12-08 | Air conditioning system capable of balancing refrigerant amount |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201569204U (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102262002A (en) * | 2011-04-20 | 2011-11-30 | 广东机电职业技术学院 | Automatic performance matching experimental instrument for refrigeration equipment and matching method thereof |
| CN102087057B (en) * | 2009-12-08 | 2013-01-23 | 海信（山东）空调有限公司 | Air conditioning system capable of balancing coolant amount |
| CN104215003A (en) * | 2013-06-05 | 2014-12-17 | 浙江盾安机电科技有限公司 | Reservoir and air conditioning equipment |
| CN109140845A (en) * | 2018-08-23 | 2019-01-04 | 特灵空调系统(中国)有限公司 | Liquid storage device and heat pump system with it |
| CN109186026A (en) * | 2018-11-08 | 2019-01-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Air-conditioning system and its control method |
| CN110529966A (en) * | 2019-09-09 | 2019-12-03 | 宁波奥克斯电气股份有限公司 | A kind of change coolant quantity air-conditioning system and its control method |
| WO2023040293A1 (en) * | 2021-09-19 | 2023-03-23 | 青岛海尔空调器有限总公司 | Heat exchanger, refrigeration circulation system, and air conditioner |
-
2009
- 2009-12-08 CN CN2009203167542U patent/CN201569204U/en not_active Expired - Lifetime
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102087057B (en) * | 2009-12-08 | 2013-01-23 | 海信（山东）空调有限公司 | Air conditioning system capable of balancing coolant amount |
| CN102262002A (en) * | 2011-04-20 | 2011-11-30 | 广东机电职业技术学院 | Automatic performance matching experimental instrument for refrigeration equipment and matching method thereof |
| CN102262002B (en) * | 2011-04-20 | 2013-10-30 | 广东机电职业技术学院 | Automatic performance matching experimental instrument for refrigeration equipment and matching method thereof |
| CN104215003A (en) * | 2013-06-05 | 2014-12-17 | 浙江盾安机电科技有限公司 | Reservoir and air conditioning equipment |
| CN104215003B (en) * | 2013-06-05 | 2018-07-06 | 浙江盾安机电科技有限公司 | Liquid storage device and air-conditioning equipment |
| CN109140845A (en) * | 2018-08-23 | 2019-01-04 | 特灵空调系统(中国)有限公司 | Liquid storage device and heat pump system with it |
| CN109140845B (en) * | 2018-08-23 | 2020-10-02 | 特灵空调系统(中国)有限公司 | Liquid storage device and heat pump system with same |
| CN109186026A (en) * | 2018-11-08 | 2019-01-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Air-conditioning system and its control method |
| CN109186026B (en) * | 2018-11-08 | 2023-08-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Air conditioning system and control method thereof |
| CN110529966A (en) * | 2019-09-09 | 2019-12-03 | 宁波奥克斯电气股份有限公司 | A kind of change coolant quantity air-conditioning system and its control method |
| WO2023040293A1 (en) * | 2021-09-19 | 2023-03-23 | 青岛海尔空调器有限总公司 | Heat exchanger, refrigeration circulation system, and air conditioner |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102087057B (en) | Air conditioning system capable of balancing coolant amount | |
| CN201569204U (en) | Air conditioning system capable of balancing refrigerant amount | |
| US11137178B2 (en) | Cold energy recovery-type variable-capacity air-source heat pump system | |
| CN105135725B (en) | A kind of single compressor the two-stage dynamic refrigeration and cold accumulation air-conditioning system and its refrigerating method | |
| CN213841417U (en) | Multi-split system | |
| CN108679868B (en) | Self-operated multifunctional heat pump system and control method thereof | |
| CN112361669B (en) | Multi-split system and control method thereof | |
| CN203771604U (en) | Parallel type active heat-tube heat-pump air-conditioner integrated machine | |
| CN103994608A (en) | Microchannel heat exchanger and refrigerating plant | |
| CN107965853B (en) | Outdoor unit of three-pipe multi-split air conditioner system and control method | |
| CN209600211U (en) | Two-way heat exchanger with liquid storage function | |
| CN115289714A (en) | Evaporation condensation heat pump unit with hydraulic module and control method thereof | |
| CN105865071B (en) | Air-conditioning system | |
| CN201122034Y (en) | Air conditioner circulating load control device and multi-gang air conditioner circulating load control device | |
| EP3734199B1 (en) | Air-conditioner system | |
| CN217900220U (en) | Evaporation condensation heat pump unit with hydraulic module | |
| CN204254925U (en) | Heat exchange system and air conditioner with same | |
| CN105299944A (en) | Full-liquid type central air conditioning system | |
| CN204345974U (en) | Shell and tube exchanger and multifunction water-heating system | |
| CN211011723U (en) | Air conditioner and cold liquid integrated system | |
| CN203586612U (en) | Outdoor unit module of multi-split system and multi-split system with outdoor unit module | |
| CN204630185U (en) | Parallel-flow heat exchanger and there is its air-conditioner | |
| CN205002440U (en) | Cold and hot balancing unit of heat pump water heater laboratory | |
| CN203586613U (en) | Outdoor unit module of multi-split system and multi-split system with outdoor unit module | |
| CN219454305U (en) | Air-supplementing enthalpy-increasing air conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20100901 Effective date of abandoning: 20091208 |
|
| RGAV | Abandon patent right to avoid regrant |